EVAPORATIVE HEAT EXCHANGER

专利摘要:
evaporative heat exchanger with finned elliptical tubular coil assembly. a set of finned finned serpentine tubes (24, 24a, 24b, 24d) is exposed which increases the performance of the evaporative heat exchanger (26, 26a, 26b, 26c, 26d), and includes tubes (10), of preferably serpentine tubes, in the serpentine set. the tubes are provided with a generally elliptical cross section with external fins (20) formed on an external surface of the tubes. the strips are spaced substantially from 1.5 to substantially 3.5 fins per inch (2.54 cm) along the longitudinal axis (13) of the tubes, extend substantially from 23.8% to substantially 36% of the nominal diameter outer tube in height from the outer surface of the tubes and are substantially 0.018 cm (0.007 inch) thick. the tubes are provided with a center to center spacing (dh) generally horizontal and normal to the longitudinal axis of the tubes from substantially 109% to substantially 125% of the nominal outer diameter of the tube, and a spacing from center to center (dv ) generally vertical from substantially 100% to about 131% of the nominal outer diameter of the tube.
公开号:BR112013000863B1
申请号:R112013000863-6
申请日:2011-07-08
公开日:2020-12-15
发明作者:Thomas William Bugler；Davey Joe Vadder
申请人:Evapco, Inc；
IPC主号:

专利说明:

Background of the Invention
[001] The present invention relates to improvements in tubes in a coil assembly for use in an evaporative heat exchanger apparatus in which the coil assembly is intended to be mounted in a duct or plenum of the apparatus in which exchanger fluids heat exchangers, typically a liquid, usually water, and a gas, usually air, flow externally through the coil assembly to cool an internal heat transfer fluid to cool an internal heat transfer fluid that passes internally through the tubes of the serpentine set. The improvements relate to the use of tubes or pipe segments that are generally cross-sectioned in an elliptical manner, in combination with tube orientation, arrangement and spacing, and fin spacing, height and thickness, which should all of them must be carefully balanced, in such a way as to provide increased heat transfer coefficients, with an unexpectedly low drop in air pressure that produces a high volume of air, which together produce a very high heat exchange capacity.
[002] Preferably, although not exclusively, the finned tube coil assembly of the present invention that uses tubes that are finned segments with generally elliptical cross sections, is more efficiently mounted on an evaporative heat exchanger of against current so that water flows downwardly and externally through the coil assembly while the air moves upward and externally through the coil assembly. The coil assembly of the present invention can also be used in a parallel flow evaporative heat exchanger, in which the air moves in the same direction as the water over the coil assembly, in the same way as an evaporative heat exchanger. transverse flow, where air moves over the coil in a direction transverse to the flow of water. Evaporation of water cools the coil assembly and the internal heat transfer fluid within the tubes that form the coil assembly.
[003] The tubes can be used in any type of evaporative heat exchanger coil set made of a set of several, and preferably many, tubes that can be provided with a variety of arrangements. The tubes are preferably arranged in rows, generally horizontal, that extend through the flow path of air and water that flows externally through the coil assembly, whether the air and water are in countercurrent, parallel flow or flow paths. cross flows. The ends of the tubes can be connected to collectors or heads for proper distribution of the internal heat transfer fluid. The internal heat transfer fluid can be a heating fluid, a cooling fluid or a processing fluid used in various types of industrial processes, where the temperature of the internal heat transfer fluid needs to be modified, typically, but not exclusively , by cooling, and often, but not exclusively, by condensation, as a result of heat transfer through the pipe walls through external heat exchanger fluids.
[004] Typically, the evaporative heat exchanger apparatus uses a number of serpentine tubes for serpentine assemblies, and these serpentine tubes are often the preferred type of tubes used due to the ease of manufacture of effective serpentine assemblies from of those tubes. Although other types of tubes of the present invention are useful for the evaporative heat exchanger apparatus of the present invention, the tubes and coil assemblies of the present invention will be described primarily, without limitation, with respect to the preferred coil tubes. The following basic information is provided for a better understanding of the relationship of the pipe components and coil assembly that use coil pipes. Each coil pipe comprises a plurality of two different types of parts, "segments" and "return curves". The segments are generally straight tube parts that are connected by means of the return curves, which are the curved parts, sometimes referred to as "curvatures" to give each tube its serpentine structure. According to a preferred embodiment of the serpentine assembly of the present invention, the tubes, which can generally be of a straight structure (hereinafter referred to as "straight tubes"), or the segments of each of the serpentine tubes, are generally of elliptical cross section and the return curves can be of any desired shape and are typically generally circular, generally elliptical, generally kidney-shaped or any other sectional shape. The maximum overall horizontal dimensions of the generally elliptical segments are usually equal to, or less than, the horizontal horizontal general dimensions of the return curves, especially if the return curves are provided with a cross section Circular. If desired, the return curves can be provided with an elliptical cross section, or a kidney-shaped cross section, but it is usually easier to make the return curves with a circular cross section. The segments of the horizontally adjacent serpentine tubes are spaced in relation to each other by means of the larger horizontal cross section of the return curves when the return curves are in contact with each other, or can be spaced by means of vertically arranged spacers between the return curves, depending on the design characteristics of the evaporative heat exchanger apparatus in which the coil assemblies are used.
[005] In serpentine assemblies, straight tubes or segments of serpentine tubes are preferably arranged in generally horizontal rows that extend through the flow path of air and water that flow externally through the serpentine assembly , whether air and water are in countercurrent paths, in parallel flow or in transverse flow.
[006] Heat exchanger heat exchangers that use sets of coils that use coil tubes with segments with generally elliptical cross sections are also known, for example, as set out in US patents 4,755,331 and 7,296,620, whose exposures by present are incorporated in this context in their entirety, which are assigned to Evapco, Inc., the assignee of the present invention. These patents do not expose or consider the use of finned tubes in the coil assembly in the evaporative heat exchange environment.
[007] The tubes with fins used in dry heat exchanger coils (non-evaporative) are known and are used in view of the greater surface area provided by the fins to dissipate heat through conduction when exposed to the air that flows externally through the dry heat exchanger coil assembly. In general, the fins of these dry heat exchangers do not materially affect the air flow through the dry heat exchanger coil assembly. Finned coils are also used extensively in product coil assemblies such as refrigerators to dissipate heat into ambient air.
[008] Examples of coil assemblies for dry heat exchangers made using fins in the form of sheets or plates with holes through which pass segments that are provided with cross sections generally elliptical are exposed in the patents of Evapco, Inc., US numbers 5,425,414, 5,799,725, 6,889,759 and 7,475,719. However, these coil assemblies are not useful with evaporative heat exchangers, since the sheets or plates would adversely affect the mixing and turbulence of the air and water involved with the evaporative heat exchange that must pass externally through the assembly serpentine.
[009] Evapco, Inc. and others have used finned tube coil assemblies in evaporative heat exchangers where the pipe segments in the coil assemblies are provided with circular cross sections that include fins that extend along the length of the individual pipe segments. The segments that are provided with circular cross sections are relatively easy to provide with fins, such as by spiraling the segments with metal strips that form the fins. These finned tubes have been used in evaporative heat exchangers, but in limited circumstances and with limited success. First, round-finned tube coils have been used in heat exchangers to increase dry cooling capacity in cold water applications when not much capacity is required and when using water as an external heat exchange liquid it can result in freezing and other problems. These uses were more rare and were provided to deal with a problem, as opposed to a way of improving the main function of evaporative cooling according to the present invention. Second, although round tube finned coils have been used to improve evaporative cooling, this has not been successful. Although the presence of the fins increases the heat transfer coefficient, in previous attempts the increases were counterbalanced because the fins also caused decreased air flow over the coil, thus resulting in poorer performance.
[0010] The finned tube coil assembly of the present invention provides a number of significant advantages. The combination of the shape of the tubes, the spacing of the tubes, the height of the fins, and the number of fins per centimeter (inch) resulted in exceptional and unexpected increases in evaporative thermal performance. The geometry of the tubes and their orientation and arrangement with a coil assembly play an essential part in the turbulent mixing of air and water. The cross-sectional shape of the segments generally elliptical provides the advantages of a large amount of surface area of the tubes in a coil assembly, effective flow and heat transfer of the process fluid internally within the tubes and flow characteristics of increased air and water. With the present invention, the surprising result of less resistance to air and water passing externally through the coil assembly allows the use of a higher volume of air that provides additional thermal capacity compared to prior art systems without adding any energy from fan. The tubes provided with fins provide an increased surface area for conductive heat exchange with the tubes and assist in the turbulent mixing of the air and the water that flows externally through the coil assembly, increasing the convection heat exchange between the air and the Water. The finned tubes take up space that can impede the flow of water and air, and so it would be expected to cause a very significant lateral air pressure drop, with the need for stronger motors for the fans to move the air through the assembly coil in the heat exchanger. Nonetheless, elliptical finned tubes with a generally elliptical cross section provided with the characteristics of the present invention not only provide a careful balance of the surface area of the increased coil assembly for conducting heat exchange with any fluid flowing within the tubes and mixing and turbulence of air and water for the convection heat exchange, but it also provides a surprising reduction in lateral air pressure drop through the coil assembly, while retaining a very large increase in the transfer coefficient of external heat.
[0011] The total capacity of the coil assembly of the present invention and the evaporative heat exchangers that contain it is greatly improved under certain nominal circumstances, or even at reduced cost, compared to the increase in capacity. For example, the cost per ton of refrigeration can be reduced, for example, by replacing a coil assembly using more non-finned tubes with a coil assembly using lesser number of finned tubes of the present invention. In addition, an evaporative heat exchanger of a certain size that uses tubes without fins of the prior art can be replaced with a smaller evaporative heat exchanger according to the present invention that achieves the same, or better, thermal performance. In addition, using a coil assembly that is provided with the finned tubes of the present invention can significantly reduce the required fan energy, and for that reason the overall energy consumption, compared to a coil assembly without fins. of the same dimension.
[0012] There are several types of heat exchanger devices used in a variety of industries, from simple air conditioning in buildings to industrial processing, such as oil refining, cooling of power plants, and other industries. Typically, in indirect heat exchange systems, a process fluid used in any of these, or other, applications is subjected to heating or cooling by passing internally through a coil assembly made of heat-conducting material, typically a metal , such as aluminum, copper, galvanized steel or stainless steel. Heat is transferred through the walls of the heat conducting material of the coil assembly to the ambient atmosphere, or in heat exchanger devices, to another heat exchanger fluid, typically air and / or water that flows externally over the coil assembly where the heat is transferred, usually from the hot processing fluid internally within the coil assembly to the cooling heat exchanger fluid outside the coil assembly, whereby the internal processing fluid is cooled and the external heat exchanger fluid is heated .
[0013] In the indirect evaporative heat exchanger apparatus, in which the finned tube coil set of the present invention is used, the heat is transferred using indirect evaporative exchange, where there are three fluids: a gas, typically air (consequently, this gas will usually be referred to in this context, without limitation, as "air"), a process fluid that flows internally through a set of serpentine tubes, and an evaporative coolant, typically water (consequently, this heat exchanger liquid or external cooling will usually be referred to in this context, without limitation, as being "water"), which is distributed over the outside of the coil assembly through which the process fluid is fluid and which also contacts and mixes with air or other gas that flows externally through the coil assembly. The process fluid first exchanges the sensible heat with the evaporative liquid through indirect heat transfer between the tubes in the coil assembly, since it does not directly contact the evaporative liquid, and then the air flow and the evaporator liquid exchange. heat and mass when they come into contact with each other, resulting in more evaporative cooling.
[0014] According to other modalities, direct evaporative heat exchange can be used in conjunction with the indirect evaporative heat exchange involving the finned tube coil set of the present invention, as set out in this context in more detail below , to provide increased capacity. In the direct evaporative heat exchanger device, air or other gas and water, or another cooling liquid can be passed through a direct heat transfer medium, called wet cover filling, where water or other cooling liquid is then distributed in the form of a thin film on the extended fill surface for maximum cooling efficiency. Air and water come into contact with each other directly through the filling surface, where a small part of the distributed water is evaporated, resulting in direct evaporative cooling of the water, which is usually collected in a reservoir for recirculation over filling. wet cover and any coil set used in the device for indirect heat exchange.
[0015] Evaporative heat exchangers are commonly used to reject heat as coolers or condensers. In this way, the apparatus of the present invention can be used as a chiller, where the process fluid is comprised of a single-phase fluid, typically liquid, and often water, even though it may be a non-condensable gas under temperatures and pressures under which the device is operating. The apparatus of the present invention can also be used as a condenser, where the process fluid is a two-phase or multiphase fluid that includes a condensable gas, such as ammonia or FREON® refrigerant or other refrigerant in a condenser system under the temperatures and pressures under which the device is operating, typically as part of a cooling system where the process fluid is compressed and then evaporated to provide the desired cooling. In the event that the device is used as a condenser, the condensate is collected in one or more condensate receivers or is transferred directly to the associated refrigeration equipment having an expansion value or evaporator where the refrigeration cycle starts again.
[0016] The present invention uses a set of finned tube coils, where the claimed combination of factors of tube form, orientation, tube layout and spacing, and fin spacing, height and thickness, must all be carefully balanced, to provide increased heat transfer coefficients with an unexpectedly low pressure drop that produces a high volume of air. The combination of increased heat transfer coefficients with a high volume of air produces a very high heat exchange capacity. DEFINITIONS
[0017] As used in this context, the singular forms "um", "uma", and "o / a" include plural referents, and plural forms include the singular referent, unless the context clearly determine otherwise.
[0018] Certain terminology is used in the following description for convenience only and is not limiting. Words that designate direction such as "bottom", "top", "front", "rear", "left", "right", "side", "up", "down" designate directions in the drawings to which it is reference is made, but are not limiting with respect to the orientation in which the invention and its components and apparatus can be used. The terminology includes the words specifically mentioned above, their derivatives and words of similar importance.
[0019] As used in this context, the term “about” with respect to any numerical value, means that the numerical value has some reasonable flexibility and is not fundamental to the function or operation of the component being described or the system or subsystem with which the component is used, and will include values within plus or minus 5% of the established value.
[0020] As used in this context, the term "generally" or its derivatives with respect to any element or parameter means that the element has the basic form, or the parameter has the same basic direction, orientation or similar for the extent to which the function of the element or parameter will not be materially affected by a little bit of a change in the element or parameter. As an example and not a limitation, the segments that are provided with a “cross section in general in an elliptical way” refer not only to a cross section of a true mathematical ellipse, but also to oval cross sections or cuts more or less square cross-sections, or similar, but not a circular cross-section or a rectangular cross-section. Similarly, an element that can be described as "generally normal to" or "generally parallel to" another element can be oriented by a few degrees more or less than exactly 90 ° with respect to "generally normal" and a few steps more less than exactly perfectly parallel or 0 ° with respect to “generally parallel”, where these variations do not materially affect the function of the apparatus.
[0021] As used in this context, the term "substantially" with respect to any numerical value or description of any element or parameter means precisely the value or description of the element or parameter, but within reasonable industrial manufacturing tolerances that will not affect form detrimental to the function of the element or parameter or apparatus that contains it, but so that variations due to these reasonable industrial manufacturing tolerances are less than the variations described as being "about" or "generally". As an example and not a limitation, “fins provided with a height that extends from the external surface of the segments a distance of substantially 23.8% to substantially 36% of the nominal external diameter of the tube” does not allow variations that adversely affect performance, such that the fins will be too short or too high to allow the evaporative heat exchanger to have the desired increased performance.
[0022] As used in this context, the term "thickness" with respect to the thickness of the fins, refers to the thickness of the fins before treatment after the fins are applied to the tubes to produce the tubes with fins, such as galvanizing the fins. tubes or coil assembly using the finned tubes, as such treatment is likely to affect the nominal fin thickness, the nominal fin height and the fin fin spacing. In this way, all the dimensions exposed in this context are of the finned tubes before any further treatment of the finned tubes themselves or any set of coils that contain them.
[0023] As used in this context, where specific dimensions are present in inches and in parentheses in centimeters (cm), the dimensions in inches control, in the same way that the dimensions in centimeters were calculated based on the dimensions in inches by multiplying the inch dimensions 2.54 cm per inch and rounding the dimensions in centimeters to no more than three decimal positions. Brief Summary of the Invention
[0024] The present invention relates to an improvement in an evaporative heat exchanger that comprises a plenum having a longitudinal geometric axis in a generally vertical manner, a distributor for distributing an external heat exchanger liquid into the plenum, a motor of air to make the air flow in one direction through the plenum in a direction generally countercurrent to, generally parallel to, or generally transverse to the longitudinal geometric axis of the plenum, and a coil assembly having a main plane and is mounted inside the plenum in such a way that the plane is generally normal to the longitudinal geometric axis of the plenum and in such a way that the external heat exchanger liquid flows externally through the coil assembly in a flow direction generally vertical, in which the coil assembly comprises inlet and outlet manifolds and a plurality of tubes connecting the manifolds, with the tubes extended in a generally horizontal direction and having a longitudinal geometric axis and a cross section of a generally elliptical sectional shape provided with a main geometric axis and a minor geometric axis where the mean of the main geometric axis length and the length of the smaller geometric axis is a nominal external diameter of the tube, the tubes being arranged in the coil assembly in such a way that the adjacent tubes are generally spaced vertically in relation to each other within planes generally parallel to the main plane , the adjacent tubes in the planes generally parallel to the main plane being staggered and spaced with respect to each other generally vertically to form a plurality of horizontal levels generally staggered in which a tube but a tube are not aligned at the same level in a general horizontal way, in a general way parallel to the main plane, and wherein the tubes are spaced from one another generally horizontally and generally normal to the longitudinal axis of the tube.
[0025] The improvement comprises tubes with external fins formed on an external surface of the tubes, in which the fins have a spacing of substantially 1.5 to substantially 3.5 fins per inch (2.54 cm) along the geometric axis longitudinal length of the tubes, the fins having a height that extends from the outer surface of the tubes a distance of substantially 23.8% to substantially 36% of the nominal outer diameter of the tube, with the fins having a thickness of substantially 0.007 inch (0.018 cm) to substantially 0.020 inch (0.051 cm), with tubes having a center to center spacing generally horizontal and generally normal to the longitudinal geometric axis of the tubes from substantially 100% to substantially 131 % of the nominal external diameter of the tube, and the tubes having horizontally adjacent spacing from center to center generally vertical of substantially 110% at is substantially 300% of the nominal outer diameter of the tube.
[0026] Preferably, the tubes are serpentine tubes that are provided with a plurality of segments and a plurality of return curves, the return curves being oriented in generally vertical planes, the segments of each tube connecting the curves return of each tube and extending between the return curves in a generally horizontal direction, the segments having a longitudinal geometric axis and a generally elliptical cross-section having a main geometric axis and an axis smaller geometrical where the average of the length of the main geometrical axis and the length of the minor geometrical axis is a nominal external diameter of the tube, the segments being arranged in the coil assembly in such a way that the segments of the adjacent tubes are generally spaced vertically each other within planes generally parallel to the main plane, with adjacent pipe segments in one mane planes general angles parallel to the main plane being staggered and spaced with respect to each other in a general manner vertically to form a plurality of stepped levels in a generally horizontal manner each segment segment is not aligned at the same level in a generally horizontal manner in a general manner parallel to the main plane, and in which the segments are generally horizontally spaced from one another and generally normal to the longitudinal geometric axis of the segment connected to the return curve.
[0027] In the case where the tubes are serpentine tubes, the improvement comprises the segments with external fins formed on an external surface of the segments, in which the fins have a spacing of substantially 1.5 to substantially 3.5 fins per inch (2.54 cm) along the longitudinal geometric axis of the segments, the fins having a height that extends from the external surface of the segments a distance of substantially 23.8% to substantially 36% of the nominal external diameter of the tube, with the fins provided from a thickness of substantially 0.007 inches (0.018 cm) to substantially 0.020 inches (0.051 cm), the segments being spaced from center to center in a generally horizontal manner and generally normal to the longitudinal geometric axis of substantially 100% segments up to substantially 131% of the nominal external diameter of the tube, and with the horizontally adjacent segments generally center-to-center vertical placement of substantially 110% to substantially 300% of the nominal outer diameter of the tube. Brief Description of the Various Views of the Drawings
[0028] The preceding summary, as well as the following detailed description of the preferred embodiments of the invention, will be better understood when read in conjunction with the accompanying drawings. For the purpose of illustrating the invention, modalities which are presently preferred are illustrated in the drawings. It should be understood, however, that the invention is not limited to the precise provisions and instruments that are illustrated.
[0029] Figure 1 is an isometric view of an embodiment of a tube with serpentine fins according to the present invention used with other of these tubes with fins in a serpentine assembly of an evaporative heat exchanger apparatus.
[0030] Figure 2 is an enlarged view of part of the serpentine tube in Figure 1, showing the area in Figure 1 within the circle designated as "Figure 2".
[0031] Figure 3 is a vertical cross-sectional view taken along lines 3-3 of the modality of Figure 2.
[0032] Figure 4 is an extreme elevation view taken along the left end of Figure 1, showing a serpentine tube having a generally vertical plane that extends 90 ° within the plane of the drawing sheet.
[0033] Figure 5A is a first mode view, partly in extreme elevation and partly in vertical cross section, of a port of four tubes of a plurality of serpentine tubes of a serpentine set, taken along lines 5- -5 of the modality of Figure 1, showing the segments generally elliptical which have their main geometric axes generally aligned vertically and generally parallel to the plane of the return curves when the tubes are generally oriented vertically as illustrated with respect to the tube in Figure 4.
[0034] Figure 5B is a view of a second embodiment, partly in extreme elevation and partly in vertical cross section, of a part of four tubes of a plurality of serpentine tubes of a serpentine set, taken along lines 5 - 5 of the modality of Figure 1, showing segments in general elliptical that have their main geometric axes of adjacent tubes at different levels angled in opposite directions with respect to each other and the plane of the return curves as illustrated in Figure 4.
[0035] Figure 6 is an isometric view of an embodiment of an exemplary coil assembly made using the finned tubes of the present invention.
[0036] Figure 6A is a schematic side elevation view of the embodiment of the exemplary coil assembly of Figure 6 manufactured using the finned serpentine tubes of the present invention.
[0037] Figure 6B is a schematic side elevation view of an alternative embodiment of an exemplary coil assembly manufactured using the finned tubes of the present invention.
[0038] Figure 6C is a schematic side elevation view of another alternative embodiment of an exemplary coil assembly prepared using the finned tubes of the present invention.
[0039] Figure 7 is a schematic vertical cross-sectional view of a first modality of a countercurrent induced air current evaporative heat exchanger, which includes an arrangement of two sets of tube coils with fins of the present invention inside the evaporative heat exchanger.
[0040] Figure 8 is a schematic vertical cross-sectional view of a modality of a countercurrent induced airflow evaporative heat exchanger, which includes an arrangement of two sets of finned tube coils of the present invention. inside the evaporative heat exchanger, with some typical components removed for clarity.
[0041] Figure 9 is a schematic vertical cross-sectional view of a modality of an induced airflow evaporative heat exchanger, which includes an arrangement of a finned tube coil assembly of the present invention located directly below of a section of heat transfer medium by direct contact that includes a wet cover fill inside the evaporative heat exchanger, with some typical components removed for clarity.
[0042] Figure 10 is a schematic vertical cross-sectional view of a modality of an induced airflow evaporative heat exchanger, which includes an arrangement of a finned tube coil assembly of the present invention located directly above of a section of heat transfer medium by direct contact that includes a wet cover fill inside the evaporative heat exchanger, with some typical components removed for reasons of clarity.
[0043] Figure 11 is a schematic vertical cross-sectional view of a modality of a countercurrent induced airflow evaporative heat exchanger, which includes an arrangement of a finned tube coil assembly of the present invention. located in a configuration spaced below the padding within the evaporative heat exchanger, with some typical components removed for clarity.
[0044] Figure 12 is a graph of test results of various modalities of an evaporative heat exchanger using coil assemblies of the present invention compared to other types of coil assemblies under equivalent conditions using test procedures such as are further exposed in this context. Detailed Description of Preferred Modalities
[0045] The present invention will be described with reference to the drawings, in which equal numbers indicate similar elements in all the different views, and initially with reference to Figures 1-4, 5A and 5B which show modalities of a finned tube, together with Figures 6, 6A, 6B and 6C, which show various modalities of a coil assembly manufactured using a number of finned tubes, as well as Figure 7, which shows a modality of an exemplary evaporative heat exchanger apparatus that contains the finned tube coil assembly of the present invention.
[0046] Although the preferred embodiments of the invention use the finned tubes of the present invention for all tubes in a coil assembly of an evaporative heat exchanger apparatus to provide the greatest advantages and benefits of the invention, and are the modalities described below in detail, other embodiments of the invention include the use of at least one tube having fins of the present invention in a coil assembly in conjunction with other tubes without fins in that coil assembly. Preferably a plurality of finned tubes, such as at least some, most preferably most, and even more preferably, as mentioned above, all tubes in a coil assembly for an evaporative heat exchanger are the finned tubes of the present invention. When finned tubes are used in this coil assembly in conjunction with finned tubes, finned tubes are used in any desired arrangement of finned tubes and finned tubes, but preferably and without limitation, finned tubes can they will usually be arranged so that they are arranged on the top part of a coil assembly and the tubes without fins may be on the bottom part of the coil assembly.
[0047] The basic component of the present invention is comprised of a finned tube 10, preferably, but not exclusively in the form of a serpentine tube better illustrated in Figures 1-4, formed to provide the advantages of the invention when combined with another of these finned tubes in a coil assembly 24 (see Figures 6 and 6A). The coil assembly 24 is having a main plane 25, which in turn is used in an evaporative heat exchanger, such as the evaporative heat exchanger 26, for example, (see Figure 7). When the finned tube 10 is in the preferred shape of a serpentine tube, it is having a plurality of generally straight segments 12 that have a longitudinal geometric axis 13 and which are interconnected by means of return curves 16. The tubes 10 can be made of any heat-conducting metal, such as galvanized steel, stainless steel, copper, aluminum or the like. Stainless steel and galvanized steel, where zinc is applied to steel to form galvanized steel after tubes are mounted in a coil assembly 24, are currently preferred materials for tubes 10 for most evaporative heat exchanger applications .
[0048] The return curves 16 can be formed integrally and in a unitary way with the segments 12 to form the tubes 10. Alternatively, the fins can be included in the segments 12 and the return curves 14, having extreme parts of connector 16 can be connected to the end connector parts 18 of the segment 12 after the fins 20 are formed on the outer surface of the segments 12. The end connection parts 16 of the return curve 14 match the shape and are typically slightly larger in the area sectional than the end connection parts 18 of the segments 12, such that the end connection parts 18 of the segments fit within the end connection parts 16 of the return curve 14, and can be substantially conveniently sealed in a substantially watertight manner to liquids and preferably substantially gas-tight, such as by welding the end connection parts 16 and 18 together. Alternatively, the end connection parts 16 of the return curves 14 match the shape and may be slightly smaller in the cross-sectional area than the end connection parts 18 of segments 12, such that the end parts of connection 18 of the segments fit over the end connection parts 16 of the return curve 14, and can be substantially conveniently sealed in a substantially liquid-tight and preferably substantially gas-tight manner, such as by welding the end connection parts 16 and 18 together. The extreme connecting parts 16 and 18 may have a shape of an elliptical shape or other cross-sectional shape. Preferably, for ease of manufacture and handling, the end connection parts 16 and 18 have a sectional shape in a generally circular manner, such that it is easier to orient and connect together with the end connection parts 16 and 18, and in such a way that uniform return curves 14 can be used, which preferably have a sectional shape in a generally circular manner over the entire curved extension, from an extreme connecting part 16 to the extreme opposite connecting part 16. However, if desired, such as to create a more closely compressed coil assembly from a plurality of tubes 10 generally arranged horizontally, the return curves can be provided with a cross section in a generally elliptical manner, where the main geometric axes of the ellipses of the body of the return curves 14 between the extreme parts of the connector 16 are oriented in one direction in a generally vertical manner, for the largest part and applications within an evaporative heat exchanger. Alternatively, the return curves 14 can be provided with a kidney-shaped cross-section over their entire length, with or without end-connection parts 16 in the form of a kidney, if the end-connection parts 18 of the segments 12 have corresponding kidney-shaped cross sections. It is preferred to connect the return curves 14 to the segments 12 after the fins 20 have been applied to the segments, for ease of manufacture.
[0049] Tubes 10 are mounted on a coil assembly 24, best illustrated in Figures 6 and 6A, where tubes 10 are coil tubes. Typically, a serpentine assembly 24 is generally globally rectangular in shape retained in a frame 28, and is made up of multiple serpentine tubes 10, where segments 12 are generally horizontal and narrowly spaced and arranged in spans on planes of generally parallel to the main plane 25 of the serpentine assembly 24. The serpentine assembly 24 is having an inlet 30 connected to a manifold or intake manifold 32, which fluidly connects the inlet ends of the serpentine tubes 10 of the serpentine assembly , and an outlet 34 connected to an outlet manifold or barrel 36, which fluidly connects to the outlet ends of the serpentine tubes 10 of the serpentine assembly. Even though inlet 30 is shown at the top and outlet 34 is illustrated at the bottom of coil assembly 24, the orientation of the inlet and outlet may be reversed, such that the inlet is located at the bottom and the outlet is located at top, if desired. The assembled coil assembly 24 can be moved and transported as a unitary structure such that it can be dipped, if desired, if its components are made of steel, into a zinc bath to galvanize the entire coil assembly.
[0050] Figure 6B is a schematic side elevation drawing of another alternative embodiment of an exemplary coil assembly 24 prepared by using the finned tubes 10 of the present invention, wherein the finned tubes 10 are generally straight tubes extending across main plane 25 (not shown). In this embodiment, an inlet 30 for the internal heat transfer or process fluid is connected to an inlet manifold or barrel 32. The internal fluid flows from the inlet manifold or barrel 32 to a plurality of finned tubes 10 that they are fluidly connected by one end to the intake manifold or barrel 32 on a higher level and within a second, header or upper barrel 33A to which the opposite ends of the tubes with upper fins 10 are fluidly connected. The internal fluid then flows from the second, collector or upper barrel 33A through a lower level of finned tubes 10 connected fluidly from one end to the second, collector or upper barrel 33A into a third, collector or intermediate barrel 33B to the to which the opposite ends of the finned tubes 10 are fluidly connected. From the third collector or intermediate barrel 33B, the internal fluid flows to an even lower level of finned tubes 10 which are fluidly connected by one end to the third collector or barrel. intermediate 33B for a fourth collector or lower barrel 33C to which the opposite ends of the finned tubes 10 are fluidly connected. Then, the internal fluid flows from the lower collector or lower barrel 33C to which at one end of the lower level of the tubes with fins 10 are fluidly connected to a collector or output barrel 36 to which they are connected fluidly attached the opposite ends of the finned tubes 10. An outlet 34 for the internal transfer of heat or process fluid is connected to the outlet manifold or barrel 36. As previously described with respect to the embodiment of Figures 6 and 6A, in the event of being desired for particular uses, the flow of the internal fluid can be reversed, such that the inlet 30 described will be an outlet and the described outlet 34 will be the inlet.
[0051] Figure 6C is a schematic side elevation drawing of an alternative embodiment of an exemplary coil assembly 24 prepared by using the finned tubes 10 of the present invention, wherein the finned tubes 10 are generally straight tubes which extend across the main plane 25 (not shown) and fluidly directly connect the respective opposite ends to an inlet manifold or manifold 32 and to an outlet manifold or manifold 36. An inlet 30 for process fluid or heat transfer internal is connected to the collector or inlet barrel 32. An outlet 34 for the process fluid or internal heat transfer is connected to the collector or outlet barrel 36. As previously described with respect to the mode of Figures 6, 6A and 6B, if desired for particular uses, the flow of the internal fluid may be reversed, such that the inlet described 30 will be an outlet and the described outlet 34 will be the inlet.
[0052] The segments 12 of the finned tubes 10 shown in Figures 6 and 6A and the finned tubes 10 generally straight as shown in Figures 6B and 6C are provided with external fins 20, which are preferably fins in spiral, which contact the outer surface of the segments 12. The fins may be serrated, may have undulations or corrugations or may be of any other widely known desired structure. If desired, collars 22 can be formed integrally and unitarily with fins 20, where collars 22 provide direct and secure contact with the surface of tubes 10 or segments 12 over a larger surface area than if only the edges of the fins 20 were in contact with the outer surface of tubes 10 or segments 12. The fins 20 and collars 22 can be formed simultaneously on tubes 10 or segments 12 using commercially available equipment in a manner known to those involved in the production of finned tubes. , and especially tubes with spiral fins. Alternatively, the fins 20, with or without collars 20, can be applied individually on the outer surface of the tubes 10 or segments 12, and then fixed, as by means of welding, in position, but this is an expensive and extremely laborious to apply fins 20 to tubes 10 or segments 12.
[0053] Preferably, the fins 20 are applied in a spiral manner in a continuous manner to the tubes 10 or segments 12 by means of conventional equipment. The fins 20 are formed from a metal band of the same type that is used for tubes 10, and the band is fed from a source of the band at a rate and in a way to be wound in a spiral around the tube 10 or segment 12 insofar as the tube 10 or segment 12 is made to advance longitudinally along its longitudinal geometric axis 13 and caused to rotate around it through the spiral fin forming equipment. When the fins 20 are wound around the tube 10 or segment 12, the inner radius of the fins 20 forms waves while the outer radius does not, which creates corrugations or minimal or notches in the fins themselves. This ripple occurs in a regular, repetitive process, in a pattern from left to right, to form ripples in and out of the plane of the material used to form the fins, not shown in Figures 2 and 3.
[0054] If collars 22 are desired, the metal band of the same type as used for tubes 10, is fed from a source of the band under a fee and in a way to be folded longitudinally to provide a flat part that it turns into collars 22 and a raised part that turns into fins 20. The folded metal band is wound in a spiral around segments 12 as the segments 12 are advanced longitudinally along and are made to rotate in around its longitudinal geometric axis 13 using the spiral fin forming equipment. When the metal strip is applied in a spiral to the segments to form the fins 20 with collars 22, the fins 20 typically have undulations in their plane and outside of it, instead of being straight as illustrated in Figures 2 and 3 for ease of illustration, while the collars 22 are flat against the surface of the segments 12, resulting from the deformation of the metal during the application of the metal strip to the segments in advance and rotation movement.
[0055] Figures 5A and 5B show the first and second respective modalities, partly in extreme elevation and partly in vertical cross section, of a part of four coil tubes 10A or 10B, for Figures 5A and 5B, respectively, of a plurality tubes 10 of a serpentine set 24, taken along lines 5--5 of the modality of Figure 1. As illustrated, starting from the left side of each of Figures 5A and 5B, the Second and fourth tubes are illustrated in a preferred orientation as being staggered in height, or vertically (as illustrated, lower), with respect to their first and third generally broadly adjacent horizontal tubes. Figures 5A and 5B also illustrate alternative modalities of orienting the main geometric axes of the segments generally elliptical 12A of the serpentine tubes 10A in Figure 5A and the segments generally elliptical segments 12B of the serpentine tubes 10B in Figure 5B. Otherwise, the modalities of Figures 5A and 5B are similar to each other. In Figures 5A and 5B, the cross section of Figure 1 was selected in such a way that the fins are not illustrated or described for reasons of clarity, but the orientation of the main and minor axes of the segments in general elliptical must be understood as a reference the total length of the finned segments 12 until they connect with or are formed unitarily with the return curves 14A and 14B. Although each of the return curves 14A and 14B is illustrated as having a circular sectional shape, as explained above, the return curves 14A and 14B can alternatively have a cross section with the shape of generally elliptical, a sectional shape generally kidney-shaped, or other cross-sectional shape. For ease of explanation, the orientation of the main geometric axes of the finned segments generally elliptical 12A and 12B will be described in the preferred modes of the serpentine tubes 10 as shown in the mode illustrated in Figures 6 and 6A, but in principle, the same orientation can be, and preferably is, provided for the finned tubes 10 in a generally straight and generally elliptical manner used in a coil assembly such as the coil assemblies that are shown in Figures 6B and 6C.
[0056] In the two Figures 5A and 5B, the segments 12A or 12B of the adjacent tubes are generally spaced vertically in relation to each other within planes generally parallel to the main plane 25 of the serpentine assembly 24 at the respective levels generally upper horizontal LIA and L1B and generally lower horizontal levels L2A and L2B. In this way, the segments 12A or 12B of the adjacent tubes 10A or 10B are situated in planes generally parallel to the main plane 25 and are staggered and spaced with respect to each other in general vertically to form a plurality of levels of a generally staggered horizontal in which each segment without segment is not aligned at the same level in a generally horizontal manner in general parallel to the main plane 25.
[0057] In the first embodiment of Figure 5A, the generally elliptical segments 12A have their main geometric axes generally vertically aligned and generally parallel to the plane of the return curves 14A when the tubes 10A are one generally vertically oriented as illustrated with respect to tube 10 in Figure 4. This alignment or orientation is regardless of whether the segments are at an upper vertical level in a general horizontal LIA or a lower horizontal level, such as the level of a general adjacent horizontal manner following L2A.
[0058] According to the second embodiment of Figure 5B, the generally elliptical segments 12B have their main geometrical axes of the tubes 10B at generally adjacent horizontal levels following LlB and L2B, angled in opposite directions with respect to plane of the return curves 14B when tubes 10B are generally vertically oriented as illustrated with respect to tube 10 in Figure 4. As shown in Figure 5B, according to a preferred embodiment where the main geometric axes of the segments 12 are oriented in opposite directions on the adjacent horizontal levels, the angle of all major geometrical axes in a first level of a generally horizontal L1B is about 20 ° with respect to the plane of the return curves and the angle of all geometrical axes main at the level of a generally horizontal adjacent next L2B is about 340 ° with respect to the plane of the return curves. According to this configuration, at each horizontal level L1B, the main geometrical axes of all segments 12B are oriented in the same angled direction and at the next lowest adjacent level L2B, the main geometrical axes of all segments are oriented in the same angled direction. , but in an opposite angled orientation in relation to the angled orientation of the main geometric axes at the L1B level. Where the main geometrical axes are angled in opposite directions at the adjacent horizontal levels, they are sometimes known as a “ric-rac” arrangement or orientation, and this term is used in the Table exposed below to designate this type of arrangement or orientation. However, if desired, at each L1B or L2B level, the main geometric axes of the segments within the same level in a generally horizontal manner can be angled in opposite directions.
[0059] Thus, as shown in Figures 5A and 5B, the main geometric axes of the finned segments 12A or 12B in a first level in a generally horizontal L1A or LlB, respectively, can be 0 ° to about 25 ° degrees from the plane of the return curves and the angle of the main geometrical axes of the segments with fins 12B or 12A, respectively, at the level of generally adjacent horizontal next L2B or L2A, respectively, can be about 335 ° to 360 ° in relation to the plane of the return curves. Figure 4 shows the main geometric axes opposed to the finned segments 12 as described with respect to Figure 5B for a complete serpentine tube 10.
[0060] The return curves 14, 14A and 14B are illustrated as being of general circular cross-section. The outer diameter of the circular cross section of the return curves substantially equals the nominal outer diameter of the tube which is an average of the lengths of the main and minor axes of the segments 12, 12A and 12B which have a cross section in general elliptical. Preferably, but without any limitation, the outside diameter of the return curves and the nominal outside diameter of the tube are about and preferably substantially 1.05 inches (2.67 cm), where the wall thickness of the forming tubes of the segments 12 and the return curves 14 is about 0.055 inch (0.14 cm). The minor geometric axis of the tube generally elliptical 10 or segments 12, 12A and 12B is about 0.5 to about 0.9 times, and preferably about 0.8 times the nominal outside diameter of the tube. In this way, the tubes 10 and straight segments 12, 12A and 12B generally elliptical equipped with a nominal external diameter of the tube of 1.05 inches (2.67 cm), will have a smaller geometric axis length of about e preferably substantially 0.525 inch (1.334 cm) to about and preferably substantially 0.945 inch (2.4 cm), and preferably about and preferably substantially 0.84 inch (2.134 cm). Tubes 10 with these dimensions have been shown to have a perfect balance between an internal diameter or appropriate dimensions to allow the processing fluid in the form of any desired gas or liquid to flow easily into tubes 10, the proximity of that processing fluid to the wall tube for good heat transfer through the tube walls with an elliptical cross-sectional shape that has an effective wide surface area, and the ability to provide the appropriate number of tubes 10 to be packed in a coil assembly 24. The tubes are robust, durable and when in the form of a serpentine, capable of being easily worked, including the connection of segments 12 and return curves 14 and placement within a serpentine assembly 24. Depending on the environment and the intended use of the heat exchangers evaporative heat exchangers, such as the evaporative heat exchanger 26, in which the finned tubes 10 of the present invention are placed, the dimensions and cross-sectional shape of the tubes 10 can be varied considerably.
[0061] The spacing and orientation of the tubes 10 which are generally provided with an elliptical cross-section or segments which are generally provided with an elliptical cross-section within a coil assembly 24 are important factors for the performance of the evaporative heat exchanger containing the coil assembly 24. If the spacing between the segments12 is too narrow, the flow of air and water through a turbulent mixture within the coil assembly will be adversely affected and fans with greater power will be required and there will be an increased pressure drop. If the spacing between the segments 12 is too large, then there will be fewer tubes per surface area of the main plane 25 of the serpentine assembly 24, reducing the heat transfer capacity, and it may be inappropriate, since, for example, mixing insufficient air and water, adversely affects the degree of evaporation and thus the heat exchange. The orientation of the segments 12, with particular reference to the angle of the main geometric axes of the segments, also affects the heat exchange capacity of an evaporative heat exchanger with which they are used.
[0062] The spacing of the fins 20 around the outer surface of the segments 12 is of utmost importance. If the fin spacing is excessively closed (too many fins per inch, for example), the ability of the external heat exchanger liquid and the air to promote turbulent mixing is adversely affected and the fins 20 can block the space externally of the coil assembly 24, such that greater air motor power is required. Similar problems involve determining the greater importance of the height of the fins (the distance from the nearest point where the base of the fins 20 contacts the outer surface of the segments 12 and the terminal tip of the fins). Even though the larger fins have more surface area than the evaporation water can cover, the longer fins can block the air passage. The thicker fins 20 also have similar major problems. The thicker fins are more durable and have a better ability to withstand the forces of water and air, as well as other material that can be dragged when they pass through a coil assembly, but thicker fins can also block the flow of air. water or air through the coil assembly and will be more expensive to manufacture. All of these factors adversely affect performance.
[0063] If the fin spacing is too large (not enough fins per inch (centimeter), for example), the advantages of a sufficient number of fins 20 for the evaporating water to cover will not be present and a detrimental effect on the mixture may occur of water and air responsible for efficient evaporation. Similar concerns are present when the fin height is too low, as there is not enough fin structure to be covered with water, and less mixing of water and air can occur. Thinner fins may not be durable enough to withstand the hostile environment they are subjected to in evaporative heat exchangers and if the fins are too thin they may be bent during operation as they are subjected to the forces of water and air that they collide, adversely affecting the flow of both water and air. In addition, and more significantly, finer fins that transfer less heat.
[0064] The present invention was conceived and developed in view of the preceding factors of the shape, orientation, arrangement and spacing of the tubes, and spacing, height and thickness of the fins, which must all be carefully balanced, and which constituted a difficult task which required considerable testing and experience. Based on this work, the appropriate parameters of the shape, orientation, arrangement and spacing of the tubes were determined, as well as the spacing, height and thickness of the fins.
[0065] The orientation and spacing, within a coil assembly 24 and an evaporative heat exchanger, of the tubes 10 with their segments 12 and return curves 14 will be described mainly with reference to Figures 5A and 5B. The spacing from center to center DH generally horizontally (which will be generally parallel to the main plane 25 in Figure 6) and generally normal to the longitudinal geometric axis 13 of segments 12, 12A and 12B is substantially 100% up to substantially 131%, preferably substantially 106% to substantially 118%, and most preferably substantially 112% of the nominal outer diameter of the tube. The Dv spacing of the pipe or vertical straight segment in general is not of major importance for the performance of an evaporative heat exchanger such as the DH spacing of the pipe or horizontal segment. The segments 12, 12A and 12B have a generally vertical center-to-center spacing of substantially 110% to substantially 300% of the nominal outer diameter of the tube, preferably substantially 150% to substantially 205% of the nominal outer diameter of the tube, and more preferably, substantially 179% of the nominal outer diameter of the tube. This spacing from center to center in a generally vertical manner is indicated by means of the distance Dv between the generally horizontal upper levels L1A and L1B and the lower generally horizontal levels L2A and L2B, respectively.
[0066] These parameters can be applied as follows to the presently preferred modality, where the nominal external diameter of the tube is substantially 1.05 inches (2.67 cm). The DH center-to-center spacing of tubes 10 or 12, 12A and 12B straight fins with tubes fins with serpentine fins 10 will be substantially 1.05 inches (2.67 cm) to substantially 1.38 inches (3.51 cm), of preferences substantially 1.11 inches (2.82 cm) to substantially 1.24 inches (3.15 cm), and more preferably substantially 1.175 inches (2.985 cm). The finned tubes 10 or the finned segments 12,12A and 12B will have a decent center-to-center Dv spacing generally from substantially 1.15 inches (2.92 cm) to substantially 3.15 inches (8.00 cm), preferably substantially 1.57 inches ( 3.99 cm) to substantially 2.15 inches (5.46 cm), and more preferably substantially 1.88 inches (4.78 cm). According to some modalities, the main geometric axes of the finned tubes 10 or finned segments 12, 12A are substantially vertically oriented, so that they are generally parallel to the plane of the return curves 14, as found illustrated in Figure 4. According to other modalities, the main geometric axes of the finned tubes 10 or finned segments 12B can be greater than 0 ° to about 25 °, and preferably about 20 °, in relation to the plane of the return curves 14 and the angle of the main geometric axes of the finned tubes 10 or of the finned segments 12B at the level of the next generally vertically adjacent horizontal level, can be about 335 ° to less than 360 °, and from preferably about 340 ° in relation to the plane of the return curves 14, such that the main geometric axes of the finned tubes 10 or finned segments 12 are oriented in opposite directions at the ho levels vertically adjacent rhizontal.
[0067] The parameters relating to the fins 20, namely, fin spacing along the longitudinal geometric axis 13 of the segments 12, the height of the fins from the outer surface of the segments 12 and the thickness of the fins are as follows according to the present invention.
[0068] The fins 20 are preferably spiral fins and have a spacing of substantially 1.5 to substantially 3.5 fins per inch (2.54 cm) along the longitudinal axis 13 of the segments 12, preferably substantially 2.75 to substantially 3.25 fins per inch (2.54 cm) and more preferably substantially 3 fins per inch (2.54 cm). Alternatively expressed, the distance from center to center between the fins is therefore substantially 0.677 inch (1.694 cm) to substantially 0.286 inch (0.726 cm), preferably substantially 0.364 inch (0.925 cm) respectively to substantially 0.308 inch (0.782 cm), and more preferably substantially 0.333 inch (0.846 cm).
[0069] The fins 20 have a height of substantially 23.8% to substantially 36% of the nominal outer diameter of the tube, preferably substantially 28% to substantially 33% of the nominal outer diameter of the tube, and most preferably substantially 29.76 % of the nominal external diameter of the tube. These parameters can be applied as follows to the presently preferred embodiment, where the nominal external diameter of the tube is substantially 1.05 inches (2.667 cm). In this embodiment, the fins 20 have a height of substantially 0.25 inch (0.635 cm) to substantially 0.375 inch (0.953 cm), preferably substantially 0.294 inch (0.747 cm) to substantially 0.347 inch (0.881 cm), and most preferably 0.3125 inch (0.794 cm).
[0070] The fins 20 have a thickness of substantially 0.007 inch (0.018 cm) to substantially 0.020 inch (0.051 cm), preferably substantially 0.009 inch (0.023 cm) to substantially 0.015 inch (0.038 cm), and most preferably substantially 0 .01 inch (0.025 cm) to substantially 0.013 inch (0.033 cm). As noted earlier in the “Definitions” section, dimensions for the thickness of the fins are applied to the fins on the finned tubes before any further treatment of the finned tubes themselves or any coil set containing them. In the case where the finned tubes or coil set are subjected to further treatment, typically by galvanizing the finned steel tubes or more typically, the galvanizing of the entire coil set containing them, the fin thickness increases the thickness of the zinc coating applied during galvanizing. Also typically, the fins after galvanizing are thicker on a base close to the outer surface of the pipe than on a tip of the terminal fins relative to the outer surface of the pipe. Since the fins are thicker after galvanizing, the spacing between the fins is correspondingly reduced. This is usually not a cause for concern with regard to the thermal performance or thermal capacity of the evaporative heat exchanger and the inhibition of rust or other corrosion obtained with galvanizing is important in the provision of finned tubes and coil assemblies with greater longevity. that if they were not galvanized.
[0071] The coil assembly 24 of any desired configuration, as illustrated in any of Figures 6, 6A, 6B or 6C, is then installed inside an evaporative heat exchanger apparatus, such as the evaporative heat exchanger 26 , as shown in Figure 7. Evaporative heat exchangers have many varied configurations, and several are illustrated schematically in Figures 7-11. Typical evaporative heat exchangers in which the coil assembly 24 of the present invention can be used are, for example, without limitation, any of the several available from Evapco, Inc., such as Models ATWB or ATC, which may include the component and operate as set out in US Patent No. 4,755,331 by Evapco, Inc. The evaporative heat exchanger apparatus, although having many variations, has the basic structure and operation described below, initially with reference to Figure 7.
[0072] Figure 7 is a vertical cross-sectional view of a modality of a counterflow current induced 26 evaporative heat exchanger, in which water flows generally vertically downward and air flows generally vertically upwardly through the plenum and coil assembly, which includes an arrangement of two sets of finned tube coils 24 of the present invention within the evaporative heat exchanger. The evaporative heat exchanger 26 is having a housing 38 that surrounds a plenum 40 having a longitudinal geometric axis generally vertical 42. One or more sets of coils 24 are mounted within the plenum 40 in such a way that the main plane 25 of each coil assembly is generally arranged normal to the longitudinal geometric axis 42 of the plenum. In this way, the generally vertical plane of the return curves 14 in the preferred embodiments using serpentine tubes 10, as shown in Figure 4 and as indicated by the generally vertical alignment of the tubes 10 in the assemblies of serpentines, as shown in Figure 7, is also generally normal to the main plane 25 of the serpentine assemblies 24 and parallel to the longitudinal geometric axis 42 of the plenum. Based on this alignment, the finned segments 12, with their longitudinal axes 13, the tubes 10 are also generally horizontally staggered planes parallel to the main plane 25 of the coil assemblies 24 and generally normal to the longitudinal geometric axis 42 of the plenum 40. If generally straight tubes with fins 10 are used as illustrated in Figures 6B and 6C, then the tubes with fins with their longitudinal axes are also generally horizontal staggered planes parallel to the main plane 25 of the assemblies of coils 24 and generally normal to the longitudinal geometric axis 42 of the plenum 40.
[0073] Air flows from the ambient atmosphere around the heat exchanger 26 through air inlets 44 that can be provided with, and preferably have, openings, or more preferably, intake air registers 45 susceptible to be closed and open selectively which can be closed or partially or fully open based on various atmospheric and operational conditions, in a widely known manner, and to protect the full 40 against inclusion of unwanted objects. In the form of Figure 7, the air is drawn into the plenum 40, passes through the coil assemblies 24 and exits through an air outlet 46 by the action of an air handler located in the air outlet housing 50. The air handler air in this embodiment is illustrated in the form of a fan 48, in the form of an impeller fan, which is preferred for use as an induced draft fan to draw air from the ambient atmosphere. Other types of fans, such as centrifugal fans, may be used, but are not usually used as draft-induced fans. A grid or screen (not shown) is placed over the fan 48 for safety reasons and to keep debris away from the fan 48 and out of the evaporative heat exchanger 26.
[0074] A bottom wall of the evaporative heat exchanger 26, together with the adjacent front, rear and side walls, defines a reservoir 52 for water or other external heat exchanger liquid. If desired, a drain pipe with an appropriate valve and a filling pipe with an appropriate valve (none of which is illustrated) can be included for draining and filling or refilling reservoir 52. The water in reservoir 52 is circulated to a liquid distributor assembly 54, which when connected distributes, through spray nozzles, holes in a tube or by means of other known devices and techniques, the water that constitutes the evaporative heat transfer liquid above the coil assemblies 24. The distributor assembly 54 is connected to one end of a conduit 56 disposed in fluid connection by the other end with the water in the reservoir. The manifold assembly 54 is typically activated or turned on when a pump 58 is turned on to pump water from reservoir 52 to manifold assembly 54 through conduit 56.
[0075] The evaporative heat exchanger 26 also preferably includes drift eliminators 60 arranged above the liquid distributor assembly 54 and below the fan 48 and air outlet 46. Drift eliminators significantly reduce water drops or mist carried in the air passing through exit 46. Many drift eliminators of various materials are found commercially available. The currently preferred drift eliminators are PVC drift eliminators available from Evapco, Inc., as set out in U.S. Patent 6,315,804, to Evapco, Inc., the disclosure of which is included in this context by reference in its entirety.
[0076] In operation, when the air is drawn into the plenum 40 through the air inlets 44 and any associated openings or dampers 45, it is also pulled through the coil assemblies 24. Water is distributed over the coil assemblies 24 by medium of the liquid distributor 54. As the air is moved upwards through the coil assemblies 24 it is mixed with the water, with an appropriate degree of turbulence as provided by means of the orientation and arrangement of the finned segments 12 that they have fins 20 with the characteristics, dimensions and parameters previously exposed. The water covers the external surfaces of the tubes 10, including the segments 12 that have the cross-section in the shape of a generally elliptical shape, as well as the fins 20. The air causes the water to evaporate, thereby cooling the water, in such a way that the cooled water exchanges heat with the tubes 10 of the coil assembly and the process fluid that is contained inside the tubes 10. Finally, the water passes through doses of coils 24 and is collected in the reservoir 52, and recycled into the liquid distributor 54 through the conductor 56 via the pump. The air with any entrained water is drawn upwards through the drift eliminators 60, in which most, and preferably almost all, of the water is removed from the air stream, before the air is discharged through the air outlet 46 through the fan 48.
[0077] As previously noted, the coil assemblies 24 which are provided with the finned tubes 10 of the present invention can be used in a wide variety and types of evaporative heat exchanger apparatus. Figures 8-11 schematically illustrate a small sample of these various evaporative heat exchangers, with some typical components illustrated in Figure 7 removed for clarity. In Figures 8-11, the components that are illustrated and that are the same as those used in Figure 7 are not described again, but are identified by numbers similar to those used in Figure 7, with the exception that and uses a letter designation common to the modalities of each of Figures 8-11, in which, for example, coil assemblies 24A are used in the evaporative heat exchanger 26A of Figure 8, coil assembly 24B is used in the evaporative heat exchanger 26B of Figure 9, the 24C coil assembly is used on the 26C evaporative heat exchanger in Figure 10 and the 24D coil assembly is used on the 26D evaporative heat exchanger in Figure 11. Any new components not used in the previous Figures are identified by a different number .
[0078] Figure 8 is a schematic, vertical cross-sectional view of a 26A forced draft, countercurrent evaporative heat exchanger, which includes an arrangement of two sets of tube coils with fins 24A of this invention within the full 40A of the evaporative heat exchanger. In this case, compared to the induced draft evaporative heat exchanger 26 of Figure 7, instead of using a propeller fan 48 mounted in the air outlet housing 50, the forced draft evaporative heat exchanger 26A of Figure 8 uses a type of centrifugal fan air mover 62 for forcing air to enter plenum 40A into housing 38A through a screen 47 covering the air inlet. The air is then generally forced vertically upwards and through the coil assemblies 24A, through which water is generally flowed vertically downwards. Thereafter, the air moves through the 60A drift eliminators and out of the 26A evaporative heat exchanger through the 46A air outlet. The centrifugal fan 62 is typically mounted inside a lower part on one side of housing 38A adjacent to an air inlet typically covered by a screen 47. The water tank is not shown in Figure 8, but will be present below the coil assemblies 24A such that water in the reservoir is prevented from reaching the centrifugal fan 62.
[0079] Figure 9 is a schematic vertical cross-sectional view of a 26B induced draft evaporative heat exchanger arrangement that includes an arrangement of a 24B finned tube coil assembly of the present invention located directly below a section of direct contact heat transfer medium which includes a wet cover fill 64, described below, within the 40B plenum of the evaporative heat exchanger. In the evaporative heat exchanger 26B of Figure 9, the air is drawn into the plenum 40B through an air inlet 44B and any associated openings or dampers 45B, where the air inlet 44B is arranged laterally adjacent to the coil assembly 24B . The evaporative heat exchanger 26B of Figure 9 differs in a first aspect with respect to the evaporative heat exchanger 26 of Figure 7, in that the air drawn through the coil assembly 24B in a generally normal, transverse or horizontally with respect to the water flow in a generally descending vertical manner through coil assembly 24B, known in the industry as a cross flow arrangement. The mixing and turbulence of air and water externally through coil assembly 24B in a cross-flow arrangement is somewhat different, but still fully effective compared to the mixing and turbulence of air and water externally through coil assembly 24 of Figure 7 in a countercurrent arrangement.
[0080] The evaporative heat exchanger 26B in Figure 9 differs in a second aspect with respect to the evaporative heat exchanger 26 in Figure 7 in that the evaporative heat exchanger 26B in Figure 9 includes a contact heat exchange section direct that contains a Wet Cover Filling 64 below the liquid distributor 54B and above the coil assembly 24B, which provides direct, evaporative heat exchange when air flow and evaporative water or other cooling liquid comes into direct contact with each other and are mixed with a certain degree of desired turbulence within the wet cover fill 64 resulting in additional evaporative cooling. The turbulent mixture of air and water in wet cover filling 64 allows for greater heat transfer between air and water, but the benefits of increased turbulent mixing in wet cover filling 64 must not be outweighed by the potential detrimental effects of requirements of a fan motor or larger fan size or reduced airflow. As noted earlier, there is a delicate balance between these factors when deciding whether and what type of wet cover filler heat transfer medium should be used. That is why the use of wet cover fill 64 is optional in the evaporative heat exchanger using the coil assembly of the present invention. The wet cover filling can be any standard filling medium, such as plastic filling, typically PVC, as well as wood or ceramic filling means, or any other filling means known in the art. The presently preferred fillers are comprised of the EVAPAK® PVC filler, from Evapco, Inc., set out in U.S. patent 5,124,087, from Evapco, Inc., the disclosure of which is hereby incorporated by reference in this context in its entirety. When wet cover fill 64 is used, it can be located above coil assembly 24B as shown in Figure 9, or below coil assembly 24C as shown in Figure 10, since in any location, the additional heat transfer in the wet cover filling 64 will additionally evaporate cool the water drained into the 52B or 52C reservoir.
[0081] In the embodiment of Figure 9, shutters 65 are built on the inlet side of the wet cover fill 64, such that air can be drawn through the shutters 65 into the wet cover fill in a cross-flow fashion , as previously described with respect to the cross flow arrangement with respect to coil assembly 24B.
[0082] The evaporative heat exchanger mode 26B in Figure 9 operates as shown below. Ambient air in the environment of the evaporative heat exchanger is drawn into the 40B plenum through the air intakes 44B and any associated shutters or dampers 45B, and in a manner of externally crossed flow through the coil assembly 24B, through which water, previously cooled when filling wet cover 64 of the heat exchanger section by direct contact, it flows externally in a general manner vertically in a downward direction. Ambient air is also drawn to fill wet cover 64 in a cross-flow manner with respect to water that generally flows vertically downward through the shutters 65, where the water is evaporatively cooled before entering contact with coil assembly 24B below wet cover fill 64. Air is then drawn from wet cover fill 64 into 40B plenum.
[0083] The water is distributed over the wet cover filling 64 via the liquid distributor 54B in which it is initially cooled evaporatively by mixing with the air flowing through the wet cover filling 64 before being drained for coil assembly 24B in which it is mixed turbulently with air and thereafter drained from coil assembly 24B and collected in reservoir 52B. The water is recycled from the reservoir 52B into the liquid distributor 54B through the conductor 56B via the pump 58B. The air, with any entrained water, at the 40B plenum is drawn upwards through the drift eliminators 60 (not shown in Figure 9) by means of the fan 48B in the air outlet housing 50B, before the air is discharged through the air outlet. air 46B.
[0084] Figure 10 is a schematic vertical cross-sectional view of another embodiment of a 26C induced draft evaporative heat exchanger that includes an arrangement of a 24C finned tube coil assembly of the present invention located directly above a section of direct contact heat transfer media that includes filling the wet cover 64C within the full 40C of the evaporative heat exchanger. The evaporative heat exchanger mode 26C of Figure 10 operates as shown below. A portion of the ambient air in the environment of the evaporative heat exchanger is drawn into the appliance through an inlet 44C arranged on top of the appliance aligned above the 24C coil assembly and flows externally downwards through the coil assembly in a direction of one. generally vertically in countercurrent with the flow of water distributed over the coil assembly through the liquid distributor 54C. Another part of the ambient air is also drawn into the appliance through the heat exchanger section by direct contact that contains the filling of wet cover 64C through the optional shutters 65C. The air that moves through the wet cover fill 64C moves in a cross-flow manner to the water that is drained generally vertically from the 24C coil assembly.
[0085] Water is distributed over the 24C coil assembly through the 54C liquid distributor in which it is mixed with the air flowing countercurrently, thereby being evaporatively cooled in the coil assembly, exchanging heat with the assembly of serpentine 24C, before being drained in and through the filling of wet cover 64C. In the filling of wet cover 64C, the water is still mixed in a turbulent way with the transversal air flow in which it is still cooled in an evaporative way, and after that it is drained from the filling of wet cover 64C and collected in the 52C reservoir. The water is recycled from the reservoir 52C into the liquid dispenser 54C through the conductor 56C through the pump 58C. The air with any entrained water is drawn into the 40C plenum and then carried upward through drift eliminators 60 (not shown in Figure 10) through the 48C fan in the 50C air outlet housing, before the air is discharged through of the 46C air outlet.
[0086] Figure 11 is a schematic vertical cross-sectional view of a modality of a countercurrent 26D evaporative heat exchanger, of induced draft, which includes an arrangement of a tube coil assembly with fins 24D located in a spaced configuration located below the wet cover fill 64D within the 40D plenum in the 38D housing on the evaporative heat exchanger.
[0087] The modality of the 26D evaporative heat exchanger in Figure 11 operates as shown below. The air in the environment of the evaporative heat exchanger is pulled into the 40D plenum through the 44D air inlets and any associated shutters or dampers 45D, and then is drawn into the 64D wet cover fill in a countercurrent manner with respect to the water that generally flows vertically downward through the wet cover fill64D. The liquid dispenser 54 (not shown in Figure 11), located above the 64D wet cover fill and below the drift eliminators (not shown in Figure 11), distributes the water over the 64D wet cover fill into which it is mixed turbulent form with the air, being thus evaporatively cooled. Then, the chilled water is drained over the 24D serpentine joint, exchanging the heat with the 24D serpentine joint, before being drained and collected in the 52D reservoir. If desired, water that is drained from the wet cover fill64D can be concentrated to flow directly onto the 24D serpentine assembly as set out in US Patent No. 6,598,862, by Evapco, Inc., the exposure of which is hereby incorporated by reference in this context, in its entirety, to more efficiently direct the chilled water to the 24D coil assembly. Water is recycled from reservoir 52D to liquid dispenser 54 through conductor 56 (not shown in Figure 11) via pump 58 (not shown in Figure 11). The air with any entrained water is drawn upwards through the drift eliminators by means of the 48D fan in the 50D air outlet housing, before the air is discharged through the 46D air outlet.
[0088] The performance of the evaporative heat exchanger is measured by the amount of heat transfer, typically, but not exclusively, during refrigeration. Measurements are carried out by means of several factors. First, measurements are carried out by means of the quantity and temperature of the process fluid that flows internally through the tubes 10 of the coil (s) set (s) of the apparatus 24 and of the water or other cooling fluid that flows externally through the coil assembly. Flow rates are measured using flow meters and temperature is measured using thermometers. The rate and temperature of the air flowing through the system is also important, as well as the force required to drive the air mover 48 that moves the air through the apparatus. Air flow is typically measured using an anemometer in feet per minute through a tube, although other widely known air flow measurement devices can also be used, and is typically determined by the rate of the fan drive motor of the air mover, usually expressed in horsepower (HP).
[0089] According to an embodiment of the evaporative heat exchanger apparatus that uses the sets of coils 24 that are equipped with the finned tubes 10 of the present invention, typically, without limitation, the process fluid, in the form of water, it is pumped into the inlet 30 and flows internally through the coil assembly at a rate of approximately 0.75 gpm to approximately 16.5 gpm per pipe present in the coil assemblies, and preferably approximately 10 gpm per pipe. The amount and rate of water that passes externally through the coil assembly (s) 24 delivered through the water supply conduit 56 as distributed through the liquid distributor 54 is approximately 1.5 gpm / square foot up to approximately 7 gpm / square foot of flat area of the determined coil with respect to the main plane 25, and is preferably approximately 3 gpm / square foot up to approximately 6 gpm / square foot. The evaporative heat exchanger apparatus using the coil assemblies 24 which are provided with the finned tubes 10 of the present invention typically, but without limitation, are provided with an air flow rate of approximately 91.44 meters (300 feet) ) per minute to approximately 228.6 meters (750 feet) per minute, and preferably approximately 182.66 meters (600 feet) per minute to approximately 198.12 meters (650 feet) per minute. The power of the fan motors is dependent on the size of the evaporative heat exchanger housing, the size of the coil assemblies used, the number and configuration of tubes in the coil assemblies, the number of coil assemblies used, the presence and orientation of any optional wet cover fill, the size and type of fan used, and various other factors, so that absolute values cannot be displayed for the required fan motor power. In general, and without limitation, the power of the fan motors varies within a very wide range, such as approximately 0.06 HP to approximately 0.5 HP per square foot of the flat area of the coil assemblies used in the heat exchangers. evaporative heat, corresponding to the area of the main plane 25 coextensive with the length and width of the coil assembly.
[0090] In the evaporative heat exchanger apparatus that uses the tube coil sets with fins 24 of the present invention, it was found that the performance is increased by means of an increase in the air flow rate even when compared to coil sets similar that use tubes provided with segments 12 with a cross-section generally shaped elliptical, but do not contain the fins 20 of the present invention. In view of the space occupied by the fins 20 in the segments 12 of the tubes 10 used in the coil assemblies 24 of the present invention, it would be expected that the flow rate would have decreased, since the fins 20 would be expected to block the flow of both air and water, so it was unexpected and surprising when the rate of air flow was increased. The increase in the air flow rate provided a surprising increase in thermal performance in the evaporative heat exchanger using the coil assemblies with the finned tubes 10 of the present invention.
[0091] The increased thermal performance of the evaporative heat exchanger apparatus using the coil assemblies 24 provided with finned tubes of the present invention will be described in greater detail with respect to the following non-limiting test procedure in which various sudden sets, including those of the present invention, were tested. under equivalent test conditions.
[0092] The test procedure included mounting several single coil assemblies in a counter-current, induced draft, evaporative cooler, Evapco, Inc. Model ATWB, in a test facility. The general layout of the counter-current, induced draft, Model ATWB evaporative cooler is shown in Figure 7, with the exception that only one set of serpentine24 was used, instead of two sets of serpentines 24 as shown in Figure 7. tested coil assemblies all had a flat area of 6 feet (1.83 m) in length (corresponding to the coil tubes provided with segments with return curves fitting within frames of this length with appropriate spacing) by 4 feet (1, 22 m) wide (corresponding to 37 adjacent tubes that were packed within frames of this width with the appropriate spacing) and had ten rows of segments 12 generally horizontal with cross-sectional shapes generally elliptical connected by means of return curves endowed with a circular cross-sectional shape, where the main geometric axes of the segments were arranged according to various ias guidelines. All tested coil assemblies used tubes with return bends with an outer diameter of substantially 1.05 inches (2.67 cm) and segments with a nominal outer diameter of the tube of substantially 1.05 inches (2.67 cm) ), with a substantially horizontal center-to-center DH spacing of 1.0625 inches (2.699 cm) (designated “Narrow” in the Table set out below) or 1.156 inches (2.936 cm) (designated “Wide” in the Table set out below) and a substantially vertical center-to-center Dv spacing of about 1.875 inches (4.763 cm). One tested coil set had no 20 fins on the segments (Test ID "A" in the Table below and in the graph in Figure 12) and represented by a baseline against which other finned coil sets were compared. Other sets of tested coils identified in the table below and in the graph in Figure 12 had spiral fins 20 with the spacing and height parameters of the fins as described and claimed in this context, and some had spiral fins 20, but did not have the parameters of spacing and height of the fins as described and claimed in this context. All coil assemblies included fins with used fins of the same thickness, namely, 0.013 inch (0.033 cm), which is within the thickness range for the fins described and claimed in this context. Some other sets of coils, namely, those that have the parameters associated with Test ID "B" and "C" (tested on a different equipment) and Test ID "D" (tested using a 5 HP motor) on the table below and in the graph in Figure 12, were tested in a different way, but the performance data presented in the graph in Figure 12 were derived using industrial calculations for standardizing performance data from devices of different configurations. The performance of coil assemblies has been tested on variable water flow rates internally through coils with water flow rates from 60 gpm to 360 gpm, water flow rates externally through coils approximately 5.9 gpm per square foot, and airflow rates from 300 feet per minute (91.44 meters per minute) to 750 feet per minute (228.6 meters per minute), generated by a fan driven by a 3 HP motor (except as previously noted with respect to Test ID "C"). The tested coil sets had the parameters as shown in the following Table:


[0093] Figure 12 is a graph of test results of coil assemblies identified in the Table on the evaporative heat exchanger under the same conditions exposed in the procedure described above, with respect to the internal process fluid (water) flow rates preferred from 6 to 9.8 gpm per tube (where each tube is identified as a “circuit” in the legend of the X axis in the graph. The graph shows curves based on heat transfer when measured in thousands of BTU / hour (MBH) against the flow of water internally through the coil assembly in gallons / minute / tube (GPM). Each curve from A to H in Figure 12 corresponds to the respective coil assembly from A to H of the Table previously exposed.
[0094] With reference to Figure 12, the baseline performance of Curve A refers to the serpentine assembly A, with a segment orientation of main geometric axes from 20 ° to 340 ° ric-rac and without fins. Curves B through F above Curve A indicate that the internal water flow rate indicated along the X axis, these curves perform better than the baseline, with gradually better thermal performance from the Curve B for Curve F.
[0095] The Test ID "G" and "H" with an orientation of main geometric axes of 20 ° -340 ° ric-rac, respective spacing of fins 1.5 and 3 fins / inch (2.54 cm) and height of 0.5 inch (1.27 cm) fin (outside the fin height parameter of the present invention) has systematically lower thermal performance (MBH) as indicated by Curves G and H, respectively.
[0096] In general, the results of the test show that an orientation of the main geometric axes of the segments generally elliptical with fins in a generally vertical direction (0 °) provides better thermal performance than a rich orientation. rac of the main geometric axes for tubes that have the same fin height and fin spacing. Nevertheless, the arrangement of the main segments in a ric-rac orientation still provides a very considerable increase in the thermal performance of a coil assembly having all other parameters within the scope of the present invention. For tubes that have the same orientation angle, that is, a rich or generally vertical orientation of the generally elliptical segments, fins that have a height of 0.3125 inch (0.794 cm) provided the best thermal performance. For tubes that are equipped with the same orientation angle as their main geometric axes and fin height, less spacing within the parameters of the present invention provides better thermal performance.
[0097] The practical effect of the results shown in Figure 12 is that the sets of coils prepared by using the finned tubes of the present invention, having the combination of tube shape factors, orientation, arrangement and spacing, and spacing, height and fin thicknesses, which must all be carefully balanced, provide an extraordinary increase in thermal capacity and performance compared to other sets of coils that have the same trail (flat area). Thus, based on the present invention, among the other benefits and advantages described above, a significantly more effective coil set can be produced by providing a smaller coil set that results in the same demand for thermal capacity. This is important not only for increased initial commercial sales, but also for more cost-effective later operation of the evaporative heat exchanger apparatus using the coil assemblies of the present invention. For sets of coils in the same flat area, the graph in Figure 12 shows very significantly increased thermal performance, for the modalities tested and the results shown in Figure 12, up to about 18.3% increase in MBH, compared to the results from the F Curve to Baseline CurveA, when measured under an internal process fluid (water) flow rate of 8 gpm per tube (calculated as 504-426 = 78/426 x 100 = 18.3%) .
[0098] It will be appreciated by those skilled in the art that changes can be made in the modalities described above without escaping its broad inventive concept. It should be understood, for that reason, that this invention is not limited to the particular modalities exposed, but that it is intended to encompass modifications within the spirit and scope of the present invention as defined by the appended claims.

权利要求:
Claims (21)
[0001]
1. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), comprising a plenum (40,40A, 40B, 40C, 40D) having a vertical longitudinal geometric axis (42, 42A, 42B, 42C, 42D), a distributor (54.54B, 54C) to distribute an external heat exchanger liquid inside the plenum, an air mover (48.48B, 48C, 48D, 62) to make the air flow in one direction through the plenum in a countercurrent direction a, parallel to, or transversal to the longitudinal geometric axis of the plenum, and a coil assembly (24,24A, 24B, 24C, 24D) having a main plane (25) and being mounted inside the plenum in such a way that the main plane is normal to the longitudinal geometric axis of the plenum and in such a way that the external heat exchanger liquid flows externally through the coil assembly in a vertical flow direction, in which the coil assembly comprises inlet (32) and outlet collectors (32) 34) and a plurality of tubes (10) connecting the collectors, the tubes extending in a horizontal direction and having a longitudinal geometric axis (13) and an elliptical cross-sectional shape having a major geometric axis with a length and a minor geometric axis with a length where the average of the length of the major geometric axis and the length of the minor geometric axis is one nominal external diameter of the tube, the tubes being arranged in the coil assembly in such a way that the adjacent tubes are vertically spaced in relation to each other within planes parallel to the main plane, the adjacent tubes in the planes parallel to the main plane being staggered and spaced in relation to other vertically (Dv) to form a plurality of levels (L1A, L1B; L2A, L2B) horizontal staggered, in which each tube is alternately aligned at the same horizontal level parallel to the main plane, and in which the tubes are spaced (DH) from each other horizontally and normal to the longitudinal geometric axis of the tube, characterized by at least one of the tubes (10) be a fin tube having external fins (20) formed on a surface external tubes, in which the fins have a spacing of 1.5 to 3.5 fins per 2.54 cm along the longitudinal geometric axis (13) of the tubes, the fins having height which extends from the external surface of the tubes a distance of 23.8% to 36% of the nominal external diameter of the tube, still having a thickness of 0.018 cm up to 0.051 cm, the tubes having horizontal (center) spacing (DH) from the horizontal to the axis longitudinal geometric (13) of the tubes from 100% to 131% of the nominal external diameter of the tube, and the horizontally adjacent tubes having spacing (Dv) from center to center of 110% to 300% of the nominal external diameter of the tube.
[0002]
2. Evaporative heat exchanger (26,26A, 26B, 26C, 26D) according to claim 1, further characterized by the fact that a plurality of tubes (10) in the coil assembly (24,24A, 24B, 24C, 24D ) tubes with fins or for most of the tubes (10) in the coil set (24.24A, 24B, 24C, 24D) be the tubes with fins, or for all tubes (10) in the coil set (24.24A , 24B, 24C, 24D) are the connecting tubes.
[0003]
3. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), according to any of the preceding claims, further characterized by the fact that the fins (20) have a spacing of 2.75 to 3.25 fins per 2 , 54 cm along the longitudinal geometric axis (13) of the tubes (10) or the fins (20) have a spacing of 3 fins by 2.54 cm along the longitudinal geometric axis (13) of the tubes (10).
[0004]
4. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), according to any of the previous claims, further characterized by the fact that the tubes (10) have a horizontal (normal) center to center spacing (DH) longitudinal geometric axis of the tubes from 106% to 118% of the nominal external diameter of the tube, or the tubes (10) have a horizontal to center spacing (DH) that is normal to the longitudinal geometric axis of the tubes of 112% of the nominal external diameter the tube.
[0005]
5. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), according to any of the preceding claims, further characterized by the fact that the tubes (10) have a 150% center-to-center spacing (Dv) up to 205% of the nominal external diameter of the tube, or the tubes (10) have a vertical center-to-center spacing (Dv) of 179% of the nominal external diameter of the tube.
[0006]
6. Evaporative heat exchanger (26.26A, 26B, 26C, 26D), according to claim 1 or 2, further characterized by the fact that the fins (20) have a spacing of 2.75 to 3.25 fins per 2.54 cm along the longitudinal geometric axis (13) of the tubes, the fins having a height of 28% to 33% of the nominal outer diameter of the tube, the fins having a thickness of 0.023 cm (up to 0.038 cm, the tubes having spacing of center to center (DH) horizontal and normal to the longitudinal geometric axis of the tubes from 106% to 118% of the nominal external diameter of the tube, and the tubes having vertical center to center (Dv) spacing of 150% to 205% of the nominal diameter outer tube or the fins (20) have a spacing of 3 fins by 2.54 cm along the longitudinal geometric axis (13) of the tubes, the fins having a height of 29.76% of the nominal outer diameter of the tube, the fins having a thickness of 0.025 cm to 0.033 cm, the tubes (10) having horizontal to normal spacing from center to center (DH) longitudinal eometric of tubes with 112% of the nominal external diameter of the tube, and the tubes having vertical center to center (Dv) spacing of 179% of the nominal external diameter of the tube.
[0007]
7. Evaporative heat exchanger (26, 26A, 26B, 26C, 26D), according to any one of the preceding claims, further characterized by the fact that the nominal external diameter of the tube is 2.67 cm.
[0008]
8. Evaporative heat exchanger (26, 26A, 26B, 26C, 26D), according to claim 1 or 2, further characterized by the fact that the nominal external diameter of the tube is 2.67 cm, the fins (20) having a center-to-center spacing of 0.726 cm to 1.694 cm, the fins having a height of 0.635 cm to 0.953 cm, the tubes (10) having horizontal to center spacing (DH) horizontal and normal to the longitudinal geometric axis (13) of the tubes from 2.67 cm to 3.51 cm, and the horizontally adjacent tubes having a vertical center-to-center (Dv) spacing of 2.92 cm to 8.00 cm.
[0009]
9. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), according to claim 8, further characterized by the fact that the fins (20) have a center to center spacing of 0.782 cm up to 0.925 cm, a height from 0.747 cm to 0.881 cm, the fins having a thickness of 0.023 cm to 0.038 cm, and the horizontally adjacent tubes (20) having vertical center to center spacing (Dv) from 3.99 cm to 5.46 cm.
[0010]
10. Evaporative heat exchanger (26,26A, 26B, 26C, 26D) according to claim 9, further characterized by the fact that the fins (20) have a center to center spacing of 0.846 cm, a height of 0.794 cm , a thickness of 0.025 cm to 0.033 cm, the tubes (10) having an unusual horizontal center-to-center (DH) spacing to the 2.985cm longitudinal geometric axis of the tubes, and the tubes having a 4.78 vertical center to center (Dv) spacing cm.
[0011]
11. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), according to any of the previous claims, further characterized by the fact that the main geometric axes of the tubes (10) are parallel to the longitudinal geometric axis (42,42A , 42B, 42C, 42D) of the plenum (40.40A, 40B, 40C, 40D) or the main geometric axes of the tubes (10) are angled with respect to the longitudinal geometric axis (42.42A, 42B, 42C, 42D) dopleno (40.40A, 40B, 40C, 40D).
[0012]
12. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), according to claim 11, further characterized by the fact that the main geometrical axes of the tubes (10) of adjacent tubes at different vertical levels (L2A, L2B ) be angled in opposite directions with respect to each other and to the longitudinal geometric axis (42, 42A, 42B, 42C, 42D) of the plenum (40, 40A, 40B, 40C, 40D).
[0013]
13. Evaporative heat exchanger (26, 26A, 26B, 26C, 26D), according to claim 12, further characterized in that the angle of the main geometric axes of the tubes (10) in a first horizontal level (L1B) is greater than 0 ° to 25 ° from the longitudinal geometric axis (42, 42A, 42B, 42C, 42D) of the plenum (40, 40A, 40B, 40C, 40D) and the angle of the main geometric axes of the tubes at the next level (L2B) horizontally vertically adjacent be from 335 ° to less than 360 ° from the longitudinal geometric axis (42, 42A, 42B, 42C, 42D) of the plenum (40, 40A, 40B, 40C, 40D) or the angle of the main geometric axes of the tubes (10) in a first horizontal level (L1B) be 20 ° from the longitudinal geometric axis (42, 42A, 42B, 42C, 42D) of the plenum (40, 40A, 40B, 40C, 40D) and the angle of the main geometric axes of the tubes in the next level (L2B) horizontally vertically adjacent is 340 ° from the longitudinal geometric axis of the plenum.
[0014]
14. Evaporative heat exchanger (26, 26A, 26B, 26C, 26D) according to any one of the preceding claims, further characterized in that the fins (20) have ripples in and out of a used material plane to manufacture the fins.
[0015]
15. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), according to claim 1 or 2, further characterized by the fact that the tubes (10) with fins are galvanized in such a way that the fins (20) after galvanizing, they are thicker on a base close to the outer surface of the tube than on a tip of the fins distal to the outer surface of the tube.
[0016]
16. Evaporative heat exchanger (26,26A, 26B, 26C, 26D) according to claim 1 or 2, further characterized in that the tubes (10) are serpentine tubes (10) having a plurality of segments (12 , 12A, 12B) and a plurality of return curves (14,14A, 14B), the return curves being oriented in vertical planes, the segments of each tube connecting the return curves of each tube and extending between the return curves in a horizontal direction, the segments having longitudinal geometric axis (13) and an elliptical cross-sectional shape having a major geometric axis with a length and a minor geometric axis with a length where the average of the major geometric axis length and the minor geometric axis length is a diameter external tube nominal, the segments being arranged in the coil assembly (24,24A, 24B, 24C, 24D) in such a way that the adjacent tube segments are spaced vertically in relation to each other within planes for parallel to the main plane (25), the segments of the adjacent tubes in the planes parallel to the main plane being staggered and spaced with respect to each other vertically (Dv) to form a plurality of horizontal staggered levels (L1A, L 1 B; L2A, L2B), where each alternating segment is aligned on the same horizontal level parallel to the main plane, and where the segments are spaced (DH) from each other horizontally and normal to the longitudinal geometric axis (13) of the segment connected to the curve of return, in which the segments (12, 12A, 12B) have external fins (20) formed on an external surface of the tubes (10), in which the fins have a spacing of 1.5 to 3.5 fins by 2.54 cm along the longitudinal geometric axis (13) of the segments, the fins having a height that extends from the external surface of the segments a distance of 23.8% to 36% of the nominal external diameter of the tube, the fins having a thickness of 0.018 cm to 0.051 cm, the segments having horizontal to center (DH) spacing horizontal and normal to the longitudinal geometric axis of the segments from 100% to 131% of the nominal external diameter of the tube, and the horizontally adjacent segments having a center to center spacing (Dv) vertical of 110% up to 300% of the nominal external diameter of the tube.
[0017]
17. Evaporative heat exchanger (26, 26A, 26B, 26C, 26D), according to claim 16, further characterized by the fact that the fins (20) have a spacing of 2.75 to 3.25 fins per 2, 54 cm along the longitudinal geometric axis (13) of the segments (12, 12A, 12B), the fins having a height of 28% to 33% of the nominal outer diameter of the tube, the fins having a thickness of 0.023 cm to 0.038 cm, the segments having horizontal to center spacing (DH) horizontal and normal to the longitudinal geometric axis of the segments from 106% to 118% of the nominal external diameter of the tube, and horizontally adjacent segments having vertical center to center (Dv) spacing of 150% up to 205% of the nominal outer diameter of the tube, or the fins (20) have a spacing of 3 fins by 2.54 cm along the longitudinal geometric axis (13) of the segments (12.12A, 12B), the fins having a height of 29.76% of the nominal external diameter of the tube, the fins having a thickness of 0.025 cm to 0.033 cm, the segments having horizontal to center (DH) spacing horizontal and normal to the longitudinal geometric axis of the segments of 112% of the nominal external diameter of the tube, and the horizontally adjacent segments having vertical center to center (Dv) spacing of 179% of the external nominal diameter the tube.
[0018]
18. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), according to claim 16, further characterized by the fact that the return curves (14, 14A, 148) have a circular cross section with an external diameter of 2 , 67 cm and the nominal tube external diameter being 2.67 cm or the return curves (14.14A, 14B) have elliptical cross-section and the nominal tube external diameter is 2.67 cm or the main geometric axes (13) the segments (12.12A, 12B) are parallel to the plane of the return curves (14.14A, 14B) or the main geometric axes of the segments (12B) are angled with respect to the plane of the return curves (14.14A, 14B).
[0019]
19. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), according to claim 18, further characterized by the fact that the main geometric axes of the segments (12B) are angled with respect to the plane of the return curves (14 , 14A, 14B), in which the main geometric axes of the segments (12B) of the adjacent tubes (10) at different vertical levels (L1B, L2B) are angled in opposite directions with respect to each other and to the plane of the return curves ( 14.14A, 14B).
[0020]
20. Evaporative heat exchanger (26,26A, 26B, 26C, 26D), according to claim 19, further characterized by the fact that the angle of the main geometric axes of the segments (12B) in a first horizontal level (L1B) is greater than 0 ° to 25 ° degrees in relation to the plane of the return curves (14.14A, 14B) and the angle of the main geometric axes of the segments in the next level (L2B) horizontally vertically adjacent is from 335 ° to less than 360 ° in relation to the plane of the return curves, or the angle of the main geometric axes of the segments (12B) in a first horizontal level (L1B) is 20 ° in relation to the plane of the return curves (14,14A, 14B) and the the angle of the main geometric axes of the segments in the next level (L2B) horizontally vertically adjacent must be 340 ° in relation to the plane of the return curves.
[0021]
21. Evaporative heat exchanger (26.26A, 26B, 26C, 26D), according to claim 20, further characterized by the fact that the fins (20) have a spacing of 2.75 to 3.25 fins per 2.54 cmao along the longitudinal geometric axis (13) of the segments (12, 12A, 12B), the fins having a height of 28% to 33% of the external diameter of the tube, the fins having a thickness of 0.023 cm to 0.038 cm, the segments having space in the center ( DH) horizontal and normal to the longitudinal geometric axis of the segments from 106% to 118% of the nominal external diameter of the tube, and the horizontally adjacent segments having vertical center to center (Dv) spacing of 150% to 205% of the nominal external diameter of the pipe , or the fins (20) have a spacing of 3 fins by 2.54 cm along the longitudinal geometric axis (13) of the segments (12.12A, 12B), the fins having a height of 29.76% of the nominal external diameter of the tube, the fins having a thickness of 0.025 cm to 0.033 cm, the segments having horizontal and normal center to centerh (DH) pairing to the longitudinal geometric axis of the segments of 112% of the nominal external diameter of the tube, and the segments having vertical center to center (Dv) spacing of 179% of the nominal external diameter of the tube.

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CN107796239B|2021-08-17|Hybrid fluid cooling method and apparatus

---

Kuvannarat et al.2006|Effect of fin thickness on the air-side performance of wavy fin-and-tube heat exchangers under dehumidifying conditions

---

CN202836266U|2013-03-27|High efficient heat exchange duct piece used for filler coupling coiled duct evaporative type condenser

---

US10132569B2|2018-11-20|Hybrid fluid cooler with extended intermediate basin nozzles

---

CN103575133A|2014-02-12|Filler coupling coil evaporative condenser

---

JP2010107130A|2010-05-13|Heat exchanger unit and indoor unit of air conditioner using the same

---

CN105651077B|2018-03-13|Improved heat-exchange device

---

CN103574965A|2014-02-12|Water chilling unit with filler coupling coiler evaporative condenser

---

CN103575132A|2014-02-12|Efficient heat exchange tube fin for filler coupling coil evaporative condenser

---

CN108474624A|2018-08-31|The thermal capacity of elliptical fin formula heat exchanger is improved

---

JP2016023925A|2016-02-08|Evaporation air conditioning system

---

CN202675721U|2013-01-16|Cold water machine group of padding coupling coil evaporative condenser

---

CN202709537U|2013-01-30|Air conditioning unit with packing coupling coil pipe evaporative type condenser

---

CN202836298U|2013-03-27|Heat exchange duct piece used for filler coupling coiled duct evaporative type condenser

---

CN205593230U|2016-09-21|Idle call evaporimeter of threading a pipe a little

---

CN106323024B|2019-01-18|Evaporative condenser

---

CN106352729A|2017-01-25|Microchannel heat exchanger and refrigeration device provided with same

---

CN215808915U|2022-02-11|Centralized heat exchange structure and air condensing units

---

JP2014047959A|2014-03-17|Heat exchanger and refrigeration cycle device having the heat exchanger mounted thereon

---

CN103574964A|2014-02-12|Air conditioning unit with filler coupling coiler evaporative condenser

同族专利:

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公开号 | 公开日

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AU2011279513A1|2013-02-28|

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CN103080687A|2013-05-01|

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PL2593741T3|2015-03-31|

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WO2012009221A3|2012-04-26|

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US20200300548A1|2020-09-24|

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US20180003443A1|2018-01-04|

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RU2013106852A|2014-08-27|

---

US20120012292A1|2012-01-19|

---

MX2013000602A|2013-06-03|

---

AU2011279513B2|2015-02-26|

---

BR112013000863A2|2016-05-17|

---

CA2805373A1|2012-01-19|

---

RU2529765C1|2014-09-27|

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EP2593741B1|2014-09-03|

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WO2012009221A2|2012-01-19|

---

EP2593741A2|2013-05-22|

---

CN103080687B|2016-04-20|

---

CA2805373C|2015-11-24|

---

ES2525165T3|2014-12-18|

引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

---

US1284578A|1918-04-10|1918-11-12|Hjalmar F Branzell|Wrought-iron ribbed pipe.|

---

US2342412A|1941-08-28|1944-02-22|Bell Telephone Labor Inc|Electron discharge device|

---

US2430210A|1945-04-17|1947-11-04|Griscom Russell Co|Method and apparatus for making finned tubing|

---

US2532239A|1948-07-23|1950-11-28|Merchant & Evans Company|Finned tube winding machine|

---

US3180405A|1959-03-11|1965-04-27|Itt|Condensers|

---

US3025685A|1960-02-03|1962-03-20|Arkla Ind|Means for wetting surfaces|

---

US3384165A|1966-02-03|1968-05-21|Du Pont|Heat exchanger|

---

US3645330A|1970-02-05|1972-02-29|Mcquay Inc|Fin for a reversible heat exchanger|

---

US4236299A|1973-03-17|1980-12-02|Balke-Durr Aktiengesellschaft|Method and device for winding spiral fins onto oval tubing|

---

NO141963L|1975-03-19|

---

SE415607B|1975-11-04|1980-10-13|Stal Laval Apparat Ab|DEVICE FOR CUTTING OF CAMFLENS PIPES IN HEAT EXCHANGER|

---

US4440216A|1980-02-18|1984-04-03|Lockheed Missiles & Space Company, Inc.|Finned heat exchanger tube|

---

BE894754A|1982-10-21|1983-02-14|Huetoetechnika Ipari Szoevetke|Combined vapour pre-cooler for refrigeration condenser - has fins with inwardly curving profile for collecting condensed moisture from air flow over serpentine coil|

---

FR2543282A1|1983-03-21|1984-09-28|Bertin & Cie|CLOSED REFRIGERANT WITH FORCED VENTILATION AND WATERTIGHT CIRCUIT|

---

US5033544A|1985-08-21|1991-07-23|Abbott Roy W|Looped fin heat exchanger and method for making same|

---

US4755331A|1986-12-02|1988-07-05|Evapco, Inc.|Evaporative heat exchanger with elliptical tube coil assembly|

---

JPH0624714Y2|1987-02-18|1994-06-29|信和産業株式会社|Square counterflow cooling tower|

---

US5092038A|1989-04-03|1992-03-03|G. P. Industries, Inc.|Method of manufacturing spiral heat exchanger tubes with an external fin|

---

US4949543A|1989-09-12|1990-08-21|Modine Manufacturing Company|Tube and fin assembly for heat exchangers in power plants|

---

US5124087A|1990-10-04|1992-06-23|Evapco International, Inc.|Gas and liquid contact body|

---

US5067322A|1990-10-05|1991-11-26|General Electric Company|Refrigerator with spine fin evaporator|

---

US5292056A|1990-12-08|1994-03-08|Gea Luftkuhler Gmbh|method of welding heat exchangers|

---

US5168923A|1991-11-07|1992-12-08|Carrier Corporation|Method of manufacturing a heat exchanger plate fin and fin so manufactured|

---

US5318112A|1993-03-02|1994-06-07|Raditech Ltd.|Finned-duct heat exchanger|

---

US5425414A|1993-09-17|1995-06-20|Evapco International, Inc.|Heat exchanger coil assembly|

---

DE4420848A1|1994-06-15|1995-12-21|Balcke Duerr Ag|Evaporative cooling tower|

---

JP3300728B2|1994-11-14|2002-07-08|三菱重工業株式会社|Heat exchanger using spiral fin tubes|

---

JP2001173977A|1999-12-10|2001-06-29|Samsung Electronics Co Ltd|Heat exchanger for refrigeration cycle and method of manufacture|

---

US6315804B1|2000-01-07|2001-11-13|Evapco International, Inc.|Drift eliminator|

---

JP4496657B2|2001-03-05|2010-07-07|パナソニック株式会社|Spiral fin tube|

---

US6598862B2|2001-06-20|2003-07-29|Evapco International, Inc.|Evaporative cooler|

---

TW563805U|2002-11-18|2003-11-21|Air Tech Co Ltd|Condenser with refrigerant coil made of copper tube having streamlined cross-section|

---

KR20040082571A|2003-03-19|2004-09-30|엘지전자 주식회사|Fin and tube solid type heat exchanger|

---

US6789317B1|2003-06-17|2004-09-14|Bechtel Bwxt Idaho, Llc|Finned tube with vortex generators for a heat exchanger|

---

US6889759B2|2003-06-25|2005-05-10|Evapco, Inc.|Fin for heat exchanger coil assembly|

---

US6766655B1|2003-10-16|2004-07-27|Ho Hsin Wu|Evaporative condenser without cooling fins|

---

US6820685B1|2004-02-26|2004-11-23|Baltimore Aircoil Company, Inc.|Densified heat transfer tube bundle|

---

RU48046U1|2004-03-26|2005-09-10|Даниленко Виктор Георгиевич|GAS PIPE BUNCH HEAT EXCHANGE PIPES GAS AIR COOLING UNIT|

---

US7717166B2|2004-05-21|2010-05-18|United Aluminum Corporation|Fin stock for a heat exchanger and a heat exchanger|

---

US7296620B2|2006-03-31|2007-11-20|Evapco, Inc.|Heat exchanger apparatus incorporating elliptically-shaped serpentine tube bodies|

---

US7913512B2|2006-04-18|2011-03-29|Wood Group Advanced Parts Manufacture, Ag|Air-heated heat exchanger|

---

US7549465B2|2006-04-25|2009-06-23|Lennox International Inc.|Heat exchangers based on non-circular tubes with tube-endplate interface for joining tubes of disparate cross-sections|

---

CN201020957Y|2006-10-08|2008-02-13|第一美卡事业股份有限公司|Improved structure of card|

---

US7475719B2|2006-12-14|2009-01-13|Evapco, Inc.|High-frequency, low-amplitude corrugated fin for a heat exchanger coil assembly|

---

JP5023911B2|2007-09-19|2012-09-12|パナソニック株式会社|Spiral fin tube heat exchanger|JP2013170802A|2012-02-22|2013-09-02|Hoshizaki Electric Co Ltd|Heat exchanger and ice making machine with the same|

---

US20140262167A1|2013-03-14|2014-09-18|Mao-Ho Kuo|Coil assembly|

---

JP5544580B1|2013-07-26|2014-07-09|株式会社エコファクトリー|Air conditioner and method of operating air conditioner|

---

CN103776278A|2013-12-24|2014-05-07|河南省法斯特散热器有限公司|Integrated core of overlong double-row circular copper pipe fins|

---

CN105264296A|2014-05-09|2016-01-20|生态工厂有限公司|Air conditioning system|

---

US10502501B1|2015-04-01|2019-12-10|Hrl Laboratories, Llc|Louvered elliptical tube micro-lattice heat exchangers|

---

DK3400412T3|2016-01-08|2021-10-18|Evapco Inc|IMPROVING THE THERMAL CAPACITY OF HEAT EXCHANGERS WITH ELLIPTIC RIBS|

---

CA3010855A1|2016-01-08|2017-07-13|Evapco, Inc.|Improvement of thermal capacity of elliptically finned heat exchanger|

---

BR112018069956A2|2016-04-01|2019-02-05|Evapco Inc|multi-cavity pipes for air overlap evaporative heat exchanger|

---

CN109073331A|2016-04-01|2018-12-21|艾威普科公司|Multi-lumen tube for air evaporation formula heat exchanger|

---

CA3031201A1|2016-07-22|2018-01-25|Evapco, Inc.|Ultra narrow channel ultra low refrigerant charge evaporative condenser|

---

US10895420B2|2016-09-01|2021-01-19|Spx Cooling Technologies, Inc.|Hybrid fluid cooler method and apparatus|

---

US10462565B2|2017-01-04|2019-10-29|Samsung Electronics Co., Ltd.|Displacement limiter for loudspeaker mechanical protection|

---

RU184599U1|2017-04-11|2018-10-31|Ришат Сафуанович Шаймухаметов|TUBE BOILER|

---

RU2646524C1|2017-04-11|2018-03-05|Ришат Сафуанович Шаймухаметов|Water tube boiler|

---

EP3410054A1|2017-05-30|2018-12-05|Ge Avio S.r.l.|Additively manufactured heat exchanger|

---

CN107976101A|2017-12-22|2018-05-01|上海发电设备成套设计研究院有限责任公司|A kind of outer fin heat exchange pipe and its application method|

---

RU183563U1|2018-04-16|2018-09-25|Федеральное государственное бюджетное образовательное учреждение высшего образования "Волгоградский государственный технический университет" |IRRIGATED HEAT EXCHANGER|

---

TWI672479B|2018-10-11|2019-09-21|國立臺北科技大學|Heat sink coil arrangement structure and cooling water tower with heat dissipation coil arrangement structure|

法律状态:
2018-12-26| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|

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2020-06-02| B06A| Notification to applicant to reply to the report for non-patentability or inadequacy of the application according art. 36 industrial patent law|

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2020-09-08| B09A| Decision: intention to grant|

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2020-12-15| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 08/07/2011, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

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申请号 | 申请日 | 专利标题

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US12/838,003|2010-07-16|

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US12/838,003|US20120012292A1|2010-07-16|2010-07-16|Evaporative heat exchange apparatus with finned elliptical tube coil assembly|

---

PCT/US2011/043351|WO2012009221A2|2010-07-16|2011-07-08|Evaporative heat exchange apparatus with finned elliptical tube coil assembly|

---